Automatic ironing machine



April 3, 1945.

A. H. GERHARDT ETAL AUTOMATIC IRON ING MACHINE Filed A ril 23, 1945 '12 Sheets-Sheet 1 wk HHWMHWWW WHM WWwwwwwwm S 1 M l l I, :R mm I m i n lm 4, 6 I I m t & I l x: h-% 4 vN H u N m\\ N\ Y 9 RN Nw Tum April 3, 1945. A. H GERHARDT ET AL 2,372,775

AUTOMATIC IRONING' MACHINE Filed April 23, 1943 12'Sheejs-Sheet 2 April 3, 1945- A. H. GERHARDT ET AL AUTOMATIC IRONING MACHINE Filed April 23, 1943 12 Sheets-Sheet 3 MN Q9 A. H.- GERHARDT ET AL 2,372,775 AUTOMATIC IRONING MACHINE v Filed April 25, 1943 12 Sheets-Sheet 5 Q N l s IL I I I I" LL I I l L III 1%zzzaa April 1945- A. H. GERHARDT ET AL 2,372,775

AUTOMATIC IRONING MACHINE Filed April 23, 1943 l2 Sheets-Sheet 6 Ap 3, 1945; A. H. GERHARDT ETAL 2,372,775

AUTOMATIC IRQNING MACHINE I Filed April 23,, 1943 12 Sheefs-Sheet "I woNv\ frag" April 3, 1945.

A. H. GERHARDT. ET AL AUTOMATIC IRONING MACHINE Filed April 25, 1945 12 Sheets-Sheet 8 J79 LE April 3,1945.

A. H. GERHARDT ET AL 2,372,775 AUTOMATIC IRONING MACHINE Filed April 25, 1945 12 Sheets-Sheet 9 i A. H. GERHARDT ET AL 2,372,775

AUTOMATIC IRONIN G MACHINE Ajaril 3, 1945.

Filed April 2:5, 1943 12 Sheets-Sheet 1o fiw wzrzwaf da I wmaa' 6%5623 5y April 3, 1945- A. H. GERHARDT EI'AL AUTOMATIC IRONING MACHINE Filed April 23, 194:

l2 Sheets-Sheet 11 April 3, 1945. A.-H. GERHARD' I" EI'AL AUTOMATIC IRdNING MACHINE Filed April 23, 1945 12 Sheets-Sheet 12 Patented Apr. 3, 19 45 UNl'iT'D STATES PATENT OFFICE AUTOMATIC IBONING MACHINE Andrew H. Gerhardt, Skokie, and- Thomas 'C.

Maher, Chicago,

Ill., assignors to Electric.

Household Utilities Corporation, Chicago, 11]., a corporation of Illinois Application April 23, 1943, Serial No.'48'4,182

20 Claims.

matic type. wherein the roll element is motor power driven, and wherein one of the elements is moved by motor power into and out of cooperating engagement with the other element. In the machine herein disclosed, the shoe element is 7 power moved into and out of cooperative engagement with the roll.

Machines of this general class have heretofore been made in two main types, one being a prtable machine of a size and weight for convenient handling and removal from place to place, or for placement for convenient use on a suitable support, such as a table or stand; and the other type being one wherein the machine proper is built in as a unitary part of, or fixedly connected to a stand, cabinet, or other suitable supporting structure. The machine constituting the present invention is shown mounted on, and constitutin a part of a supporting frame, but it is to be understood that if desired, the machine could be readily converted for use as a portable machine,

by merely relocating the main single control member.

One of the objects of this invention is to provide in an ironing machine of the character indicated, a novel drive arrangement for operating the roll and shoe independently of each other,

so that at no time is the power of the motor utilized for simultaneously operating both the roll and the shoe, thus permitting the use of a relatively small and light Weight motor.

Another object is to provide an improved drive mechanism for' an automatic ironing machine, including separate drive connections for operating the roll and. the shoe, and wherein said separate drive connections are operably connected respectively to the opposite ends of the motor shaft and are interconnected in a manner to preclude simultaneous operation of the roll and shoe.

A further object is to provide a simplified control mechanism for an automatic ironing machine, including a single control member adapted to be manipulated by the operator for selectively controlling the applicationof the power of the driving motor for actuating the roll and the shoe.

Still another object is to provide a novel and simplified operator actuated control mechanism, including a single control member, together with connections for selectively operating separate drive connections from the motor for actuating the roll and the shoe, and wherein the control member is adapted to be moved in' a cyclic manner to cause sequential operation of the shoe and 5 the roll, and byvirtue of which operation of the single control member can selectively cause any of the following effects: first, roll rotating with shoe engaged therewith; second, roll stopped with shoe engaged therewith; and third, roll stopped 10 and shoe disengaged therefrom.

And still another object is to provide an improved drive mechanism for an automatic ironer,

tions from one end of a motor for rotating the roll, together with connections by virtue of which roll, together with a novel, unitary drive mechanism adapted to be manufactured as a separate unit, and which may be quickly and easily interconnected with the roll driving connections for converting a machine of the type having a handoperated shoe into an automatic ironer, wherein the shoe is moved by motor power.

Other objects and advantages of this invention will be apparent from the following description, taken in connection with the accompanying drawings, in which:

Fig. 1 is a front elevational view of the ironin machine embodying the present invention, with parts broken away and shown in section to illustrate details of construction, andthe controls 35 in a position at which the shoe-ls engaged with the roll and the roll rotating. I I

Fig. 2 is an enlarged, vertical, sectional view of the drive mechanism for the roll, taken substantially as indicated at line 2-2 on Fi 1.

Fig. 3 is a transverse, sectional view through the driving mechanism, taken substantially as indicated at line 3-3 on Fig. 2, showing the clutch parts in a position corresponding to -a pressing condition of the machine, wherein the shoe is in engagement with the roll, and wherein th roll is stopped.

' Fig. 4 is a fragmentary sectional view of the cluitch mechanism seen in Fig. 3, showing a coning and the shoe is in pressure engagement with the roll.

Fig. 5 is a transverse sectional view through the roll drive clutch, taken substantially as indicated at line 5-5 on Fig. 4.

Fig. 6 is a vertical axial section through the the shoe may be moved toward or away from the dition of-the mechanism when the shoe is rotat-- torque applying shoe rock shaft, taken substantially as indicated at line 8-8 on Fig. 28.

Fig. 7 is a transverse, sectional view, taken at line 'I-'! on Fig. 6, showing the cam operated control for actuating the rock shaft, and associated parts shown in a position corresponding to the shoe away from the roll. and the roll stopped.

Fig. 8 is a section similar to view 1, but showing the position of the parts corresponding to the shoe in pressure engagement with the roll.

Fig. 9 is a detail, tranverse, sectional view through the torque applying rock shaft, taken as indicated at line 9-9 on Fig. 6.

Fig. 10 is a bottom elevational view of the linkage and part of the control mechanism for controlling the movement of the shoe toward and away from the roll, with the parts shown in a condition of adjustment corresponding to pressure engagement of the shoe against the roll, and with the roll rotating.

Fig. 11 is a view similar to Fig. 10 showing the position of the parts corresponding to the shoe engaging the roll, and the roll stopped.

Fig. 12 is a view similar to Fig. 10' and represents an intermediate position of the parts as occurs between the position of adjustment of the parts represented in Figs. 11 and 13.

Fig. 13 is a view similar to Fig. 10 showing the parts in a position of adjustment corresponding to the shoe out of engagement with the roll, and the roll stopped.

Fig. 14 is an end elevational view of the control linkage and shoe operating mechanism, taken substantially as indicated. at line l4-l4 onFig. 13, and corresponding to a position at which the shoe is away from the roll, and the roll stopped.

Fig. 15 is a detail view of the shoeoperating cam and associated parts, shown in another position of adjustment from that illustrated in Fig. 14, and corresponding toa position at which the shoe is against the roll, and the roll is mtating.

Fig. 16 is an enlarged, detail view of the knee control member, shown operably connected to the linkage and driving mechanism for actuating the shoe under motor power, into and out of pressure engagement with the roll, and for driving the roll.

Fig. 17 is a detail sectional view through a portion of the control linkage, taken as indicated at line I'I-H on Fig. 10.

Fig. 18 is a transverse, staggered, sectional view, with certain parts, shown in elevation, through the power drive mechanism for actuating the shoe, taken substantially as indicated at lines l8-l8 on Fig. 1, and lines iii-l8 on Fig. 19.

Fig. 19 is a sectional view through the shoe driving mechanism, taken substantially as indicated at line l9.l9 on Fig. 18, and showing the driving clutch disengaged.

Fig. 20 is a transverse, staggered, sectional view through the shoe operating mechanism, taken substantially as indicated at line 20-20 on Fig. 19.

Fig. 21 is a. fragmentary sectional view through a portion of the shoe driving mechanism, taken substantially as indicated at line 2l-2l on Fig. 19.

Fig. 22 is a transverse, axial section through the outer end of the shoe driving mechanism, taken as indicated at line 22-22 on Fig. 18.

Fig. 23 is a detail view, part in section and part in elevation, taken substantially as indicated at line 23-23 on Fig. 21.

Fig. 24 is a sectional view similar to Fig. 19, showing the clutch in engaged position.

Fig. 25 is a transverse, staggeredfragmentary, sectional view through parts of the shoe'drivlns mechanism, taken substantially as indicated at line 25-25 on Fig. 24, and showing the tripping disc and finger.

Fig. 26 is a side elevational view of the tripping disc of the shoe operating mechanism.

Fig. 27 is a face view of the tripping disc, taken as indicated at line 21-21 on Fig. 26.

Fig. 28 is a staggered, sectional view, part in section and part in elevation, through the shoe supporting arm, and associated parts, with the shoe shown in pressure engagement with the roll, and the dot line position indicating the shoe away fromthe roll.

Fig. 29 is a vertical, sectional view through the shoe arm support, taken as indicated at line 29-29 on Fig. 28.

Fig. 30 is a transverse, sectional view, part in section and part in elevation, through a portion of the emergency release mechanism, taken as indicated at line 30-30 on Fig. 28.

Fig. 31 is a View similar to Fig. 28 with the shoe supporting arm shown in section, and the emergency release in operated condition, disposing the shoe out of operative pressure engagement with the roll.

Fig. 32 is a sectional view through the shoe arm support in emergency released condition, taken substantially as indicated at line 32-32 on Fig. 31.

Fig. 33 is a sectional view similar to Fig. 30, but showing a portion of the emergency release in a released condition.

Referring now in detail to the drawings, the machine proper includes a supporting frame in the form of a hollow housing or base In, of generally rectangular form, at the right hand end of which is mounted an upstanding gooseneck type housing or standard I I, which serves to enclose power drive connections to and provides support for a rotary roll I 2. The housing I 0, is formed mainly of sheet metal, and is of a generally inverted U-shaped cross-section, connected at opposite ends to cast members III. The standard II, as shown, is in the form of a casting. and includes an upstanding, tubular portion terminating at its upper end in a horizontal extending tubular portion, and the said upstanding and horizontal portions being joined together by suitably curved surfaces The standard, II, is of relatively small CI'OSSrSECt -OHQJ dimension, and

preferably, is approximately equal to, or less than, the external diameter of the roll l2, taken at any transverse plane throughout the entire length of the standard.

The roll I 2, includes a tubular metal body l4,

around which is wrapped suitable padding material as indicated at I5, and the latter in turn is surrounded by a fabric wrapper or coverl 5 The roll extends horizontally and in parallel spaced apart relation to the top of the base I0, and i totally supported at one end by the horizontal portion of the gooseneck standard H, in a conventional manner. Cooperating with the roll 12, is a shoe l6, which is-preferably electrically heated in a manner well understood in the art. The operating faceof the shoe is shaped to the contour of the padded roll l2, and is mounted for movement into and out of pressure engagement with the roll, as will hereinafter be described.

The metal tubular bodyl4, of the roll is provided at opposite ends, and at substantially cen- 1 trally of its length, with dish-shaped stampings I1 and I8. The dish-shaped stampings H, are provided with centrally ofiset portions H formed to support bearings I9, which provide,. journal-' of the drawings, the tube 20, extends beyond the roll into the gooseneck standard H, and is interfitted into two spaced-apart bearings 'l i and H", in said horizontal portion of the standard ll. By virtue of this construction, the tube is adequately supported in the standard II, and thus provides journal-support for the roll I 2. The dished member l8, at the free or outer end of the roll is formed to provide an interlocking driving connection.

witha roll drive shaft, 22, which extends centrally and longitudinally of the roll through the tube 20, and having an end portion extending into the interior of the gooseneck standard i l, for connection to the driving mechanism, hereinafter de'- scribed, and which serves to impart driving rotary motion to the roll I2. The said end portion of the shaft within the standard I I, is provided with an oil seal 24. in engagement with the inner wall of the tube 20, and said shaft-is secured in proper position with respect to the roll I? and tube 20 by means of a spring collar 26, mounted on the shaft, adjacent theou'ter end of said tube 20.

a gear 4|, loosely mounted on-the adjacent end of a horizontally extending shaft 43, one end of which shaft is press-fitted into'a boss 44, constituting a part of the motor housing, and the other end of said shaft being slip fitted in a boss 46, formed at the outer end of the cast housing member 32, as seen in Fig. 3 of the drawings, The.

' gear 4|, has its hub provided with .an'annular groove 41, into which projects the edge of a retaining plate member 48, secured to abosson the adjacent end of the motor housing by screws '43,

Said plate thus servesto preclude axial movement of the gear 4|, on its shaft 43. Mounted on the outer fac of the -gear 4|; by means of rivets 50, is a clutchplate 5|, formed with a central opening 53, the contour of which is such as to provide three circumferentially spacedapart driving teeth 54.

' The driving mechanism for the roll is under control of a clutch mechanism which in turn is subject to interlocking control with the driving mechanism for power moving of the shoe into and out of engagement with the 'roll, as will hereinafter be described. The clutch mechanism is car- 4 of the drawings.

ried on the shaft 43, within a chamber 55, formed in the housing member 32, as seen-in Figs. 3 and mounted on the shaft 43. Said pinion is formed 'I'nreaded'into the outer end of thetube'ZO, is a nut 21,-adapted to serve as an abutment shoulder for the collar 26, to preclude outward movement 1 of the shaft with respect to the tube 20 and the standard I I. I

Roll driving mechanism The driving mechanism. for the roll l2, includes an electrically driven motor 30, disposed within the sheet metal supporting base l9, adjacent the right hand end, andhaving its housing securely connected toa cast housing member 32, by means of machine screws 33. The housing 32, serves to enclose speed reducingmech'anism and the lower portion of transmission mechanism, togethergwith clutch mechanism disposed. in registration with -the upright-leg portionof the gooseneck standard H, which mechanisms serve to supply power for operating the oil. The upper end of the cast housing member 2, ,is formed with an opening disposed in registration with the opening formed at the lower end of the standard H, which in turn is in registration with a similar opening ,formed in the top of the sheet metal housing it),

as seen in Figs. 1 and 2 of the drawings: The

with three equidistant, circumferentially spaced teeth of greater length than the other teeth of said pinion, as clearly seen in Fig. i of the drawings. so that when said pinion is axially shifted into operative engagement withthe clutch plate 5|, the three long teeth are moved into cooperating relation to the driving teeth 54. 0f the] clutch. plate 5|,and by virtue of which rotary motion'is thus transmittedto the pinion 51. The purpose of forming the clutch plate in the manner indicated, for cooperating with the three elongated or extended teeth on the pinion, is to avoid chattering and noise, and to insure quick and easy entrance of the said elongated teeth in- .to the opening in the clutch plate, intermediate 1 its teeth 54,- and thereby obtain substantially instantaneously clutching and driving relation 'of the pinion and the clutch plate. Said pinion 57, at the end opposite said teeth, is formed with an elongated hub, 58, the extreme end of which is formed with an enlarged annular flange 59,

adapted to be seated into an anular socket 60,-

formed in an enlarged flanged shoulder 6|, of a gooseneck standard is secured to the top of the I support housing by means of three circumferen tially spaced-apart machine screws-35, and the casthousing member 32, is rigidly connected to. i the lower endv of the gooseneck standard H. by means of two machine screws 31, one of which is of substantial length as seen in Fig. 2 of the draw? ings.

In the construction illustrated, power take-ofi driving connections are provided at opposite ends of'the motor shaft, and one of said connections serves to provide power for operating the roll and the other of said connections serves to supplypower for actuating the shoe i6. for, moving 'it under power into and out of cooperating engage- .ment with the roll '82; The right hand, end of the motor shaft is provided with a driving pinion 40, as seen in Fig. 2 of the drawings, meshed with clutch shifting collar 62, which likewise is slidably mounted on the shaft 43. The shoulder SI, of

.said collar is provided with anopening'of substantial angular extent to permit insertion of the flange 59, of the pinion 57, into the socket portion 80. The clutch pinion 51, and the shifting collar 62,-together with shaft 33, are assembled together by first seating the flange 59', of pinion 51, into the socket in the shoulder ii, of the collar, and then extending the shaft 43, therethrough, so as to maintain the parts in coupled relation. This connection serves to reduce transmission of rotary motion from the pinion 51, to the collar '62,

' and thereby efiects a reduction in strain and wear upon the element employed for shifting the collar 62. r

Disposed in abutting relation to the outer end of a shoulder 65, formed at the outer end of the clutch shifting collar '62, is a flanged thimble 66, surrounded by a coil spring 68, reacting against the flange of the thimble and against the end of the chamber 55 in the housing member.32, and thus serves to urge the clutch shifting collar 62,

together with the clutch pinion 51, in an axial direction toward the motor. The extent of such inward axial movement, under influence of spring 68, is limited by a crimped washer'10, mounted in an annular groove on the shaft 43, adjacent the outer flange 65, of the shifting collar, in a position to be engaged by the closed end of the thimble 66.

Meshing with the underside of the clutch pinion 51, is an idler gear 12, freely mounted on a stud 13, carried in a boss 14, formed as an extension of the motor housing. The lower portion of the housing member 32 is filled with suitable lubricant, preferably in the form of oil, the level of which desirably, should be sufiicientl'y high so ings. It will now be apparent that when the clutch pinion 51, is in cooperating engagement with the clutch plate 5I,. power and motion is transmitted through the gear train described, to the roll drive shaft 22, for effecting rotation of the roll I2. The drive mechanism above described is of relatively-simple and economical form, which lends itself to convenient manufacturing by virtue of which the gear train may be assembled as a unit upon the mounting bar 16, prior to final assembly in the machine, and

- further permits utilizing a supporting standard that the idler gear 12 continuously travels through the bath of oil and picks up the same, and transmits it to the clutch pinion 51, which in turn transmits the lubricant through the train of gears, constituting the power transmission driving mechanism described, and thus serves as the medium for lubricating such mechanism.

The gearing thus far described pertains to a speed reduction from the motor 30, to the driving pinion 51, when the latter is engaged with the clutch plate 5|. A further reduction in speed is obtained by mechanism which will now be described, and which also serves as the means for transmitting motion to drive the roll I2. This mechanism'is in the nature of a unitary gearing mounting bar 16, extending upwardly into the ipright hollow leg portion of the gooseneck standard I I, with the lower portion of the bar disposed in the housing member 32, as 'seen in Fig. l of the drawings. The opposite ends of the mounting bar 16, are reduced as indicated at 11, to provide trunnions, 'and.the lower trunnior of said bar is seated in a socket 32 formed in the housing 32, while the trunnion at the upper end of said bar is seated in a socket II formed in the interior of the upper end of the standard II, as seen in Fig. 1 of the drawings. Projecting laterally from said bar, and rigidly secured thereto, are vertically spaced-apart horizontally extending stub shafts 80, 8|, 82, 83, and 84.

r The outer end of the stub shaft 00, is fitted in a socket 32 supported in a boss on the inner wall of the housing member 32, and serves to maintain the mounting bar 16, in aligned vertical position with all of its stub shafts disposed for operating the roll, hereinafter assembly, and includes a vertically disposedin proper aligned relation with respect to the v driving pinion 51. Loosely mounted on the stub shaft 80, is a gear 86, meshed .with the clutch pinion 51, and rigidly attached to the gear 86, is a pinion 88, with which is meshed a gear 89, loosely mounted on the stub shaft 8|. Loosely mounted on the stub shaft 82, is another gear 90, which in turn is meshed with the gear 89, and rigidly attached to the gear 90, is a pinion 92, which is meshed with a gear 93, loosely mounted on stub shaft 83, and this latter gear 83, is meshed with a gear 94, loosely mounted on the uppermost stub shaft 84. These gears are confined on their respective stub shafts in any convenient'manner, and as herein shown, by means of spring U-shaped clips 16 Rigidly connected to the uppermost gear 94, of the gear train, is a coupler member 95, of thimblelike formation, the closed end of which projects outward, and is formed with a socket in the nature of a slot for receiving a tang-shaped terminal 22. formed on the adjacent end of the roll drive shaft 22, as seen in Fig. 1 of the draw- I I, of relatively small cross-sectional dimensions.

The shifting of the clutch pinion 51, by the collar 62, for controlling the drive connections to the roll I2, is subject to the operation of control apparatus, which is in the nature of a dual control, hereinafter described-which also serves to control in proper sequence, the application of power for actuating the shoe into and out of cooperative engagement with the roll. For shifting the collar 62, axiallyin controlling the operation of the clutch, there is employed a cylindrical plug or body I00, rotatably mounted in a tubular bearing provided in the housing member 32. The inner end of the plug is pro-. vided with a nubbin IOI, positioned to be moved into cooperating engagement with the flange shoulder 65, of the clutch collar 62. The plug body I00, is retained in position in the housing 32. by a retaining plate I02, secured by screws I03, to the housing member 32, with an edge portion of the plate projecting into an annular groove I00, formed in the plug body.

Rigidly connected to'the outer end of the plug body is a crank arm I05, i.n the form of a link, the outer end of which is pivotally connected by a pivot pin I01, by a lo motion connection to one end of an operating bar I06. The operating bar I06, is rigidly conn cted at its opposite end to a depending lever I08, pivotally connected at I09, to a frame member ID of the main supporting housing I0. The lower end of the lever I08, has connected thereto, a movable control member comprising a rod II I, threaded into the lower portion of the lever I08, as seen in Fig. 16 of the drawings, and rigidly connected to the lower end of-the rod III, is a depending, fiattened, knee operated member II2. Referrin now to Fig. 1 of the drawings, the knee operating member II2, normally in the starting of the machine, is in the position as indicatedby dot and dash lines at A, and is adapted to be first movedto the right to the position indicated by dot and dash lines at B, and is then adapted to be returned by the action of a coil spring I I4, connected to the lower end of the depending lever I08, and to the frame member I0", to either the position indicated by dot and dash lines at A, or to the full line position indicated in full lines in the drawings, which position. for convenience, is indicated at C." When the knee lever member H2, is moved from position A" to B," the operating bar I06 is moved about the pivot I09, so that the outer end of said bar moves in an upward direction, and by reason of the pivot pin I01, causes the crank arm I05, to move in clockwise direction, rotating the plug body I00, thereby causing the nubbin IM to react agai tthe flange 65, of the collar 62, and thereby shift the collar and the pinion 51, outwardly along the shaft 43, to disengage the pinion 51, from the clutch plate 5|. This movement takes place against the reactive force'of the coil spring 68 and spring II4. In this condition of adjustment, the driving connections-to the roll are broken by disengagement of the clutch, which comprises the three elongated teeth of the pinion member 51, and the clutch plate I, and the position of the clutch parts is then indicated in Fig. 3 of the drawings. When the knee operating lever H2, is permitted to return to the position indicated at A by spring II4, it is to be understood that the connections of the parts are such that the movement of the bar I06, and the crank arm I05, causes the clutch to remain disengaged, so that the drive connections to the roll I2, still remain inoperative. When, however, pressure against the knee 'control member H2, is further relieved, said'member assumes the full line position indicated at C in Fig. 1 of the drawings, under influence of the spring H0, at which position the operating bar I06, has moved the crank arm I05, in counter-clockwise position, and the plug I00, rotated suificiently to move the nubbin IN, to relieve its pressure engagement with the shoulder 85, of the shifting collar 62, sothat the spring 68, is free to move said collar 62, together with pinion 51, to dispose the elongated teeth of the pinion into meshing engagement with the clutch plate 5I, at which time the driving connections are established for imparting and transmitting rotary motion to the roll l2. The purpose of the slot I05, in bar I06,-is to provide freedom of movement between the outer end of the operating bar I06 and the pivot pin I01, of the crank arm I05, to accommodate the shifting relationship of the pin I01, when the crank arm I05, is moved upwardly in clockwise direction by the operating bar I06, incident to movement of the knee operating member II2, from the full line position indicated at C, to either the positions indicated at A or B," or, when the knee operating member is moved from the dot and dash outlined position A, to the position 'B. I

It is to be understood that incident to such conabutting against the outer surface of said arm. Slidably mounted in the bearing I28, is a stub shaft I30, one end of which projects through an enlarged opening I20 in the web portion of the arm I20, and rigidly attached to the outer end of said stub shaft is a handle I32.

The other end of the stub shaft I30, carries a transversely extending pin I34 on each end of which is journaled a roller I35, disposed on opposite sides of the stub shaft I30. A coil spring I38, surrounds the bearing I28, and abuts at opposite ends against the adjacent surfaces of the webs of the respective arm members I20 and I24, tending to urge the arms apart. Normally, when themay be readily manipulated by turning the ham.

dle I32 through an arc of approximately 90. degrees, from the position seen in Fig. 28 to the position seen in Fig. 31, in which position the rollers I35, are disengaged from the projections I38, and disposed-in a vertical plane, as seen in Figs. 31 and 32 of the drawings, in registration with the space between the projections I38. In such position of the parts, the spring I36,'causes separation of the arm members I20 and I24, to the position as seen in Fig.31 of the drawings. To relatch the arms in operative relation, the spring I36, is compressed simultaneously with moving the arm I20, into proper relation to the arm member I24, and disposing rollers I35, beyond the ends of the projections I38, at which time the handle I32, may be rotated approximately 90 degrees, so as to dispose the rollers I35,

in abutting relation to the ends of the projections 40 I38, which serves to latch the arms in operative trolling movement by the knee operating member I I2, there is also employed other control-apparatus by virtue of which the motor power, as will hereafter be described, is employed for moving the shoe I5, under power, into or out of operative engagement with the roll I2.

Shoe supporting structure rock shaft, intermediate the side members I20,

of the arm I20, is an upwardly extending auxiliary arm I24, adapted to be normally latched to the arm I20, as seen in Fig. 28 of the drawings,

.by means of an emergencyrelease'mechanism to be presently described. The lower end of the auxiliary arm I24, is provided with a splined bore for seating upon the splined outer end portion drawings, is disposed in a horizontal plane, and

position. The purpose of the emergency release above described, as is well known, is to permit instantaneous disengagement of the shoe from the roll in the event that the electrical current is suddenly cut off. Such a release is particularly important to insure against possible damage to articles in process of being ironed, in the event that the motor of the machine is suddenly stopped by a break in the current supply line.

The shoe rock shaft I23, asmay be seen in the is journal supported by two transversely, spaced apart bearings I40 and I. In the construction illustrated in the drawings, the shoe rock shaft proper is of relatively short length, and the shaft is desirably preloaded with springpressure, so as I 23*, of the rock shaft I23, and is fixedly secured thereon against axial movement, by me'ans of a set screw I20.

The emergency release mechanism, which normally latches the ,arm members I20 and I24 in of the drawings, includes a flanged b'earingmem:

operative relation to each other, as seen in Fig-28 to permit utilizing a motorof relatively small size and low power requirements. Referring nowto Fig. 6 of the drawings, it will be seen that the end of the rock shaft, opposite the end supporting the shoe arm, is rigidly attached, suchas by welding, to a bearing plug I43, which in turn is journaled. in the bearing I4 I. The outer end'of the bearing plug-'I43,'i ncludes a tubular-extension I43, providing journal support for one" end of an elongated tubular body I45. The opposite end" of the tubular body is telescoped over, and rigidlysecured to' a'tubular extension I48#,of a plug1I48, as by welding. The outer end of the plug I46, has press-fittedthereimia cylindrical plug I41,.'having' a portion, extending beyond the end thereof, I and journaled in a bearing I48,formed as an inte'gral part of the adjacent end casting member I0 of the main supporting housing I0. .Ihe interior of the extensions I43, of the ,plug I43 and I46 of the member I46, are provided with bores I43 and I46 respectively, of rectangular formation, for accommodating the ein, the ends of a torsion rod I50, of square cross section. The body I43, is shouldered at I43, on which is seated an arm I52, rigidly connected thereto, as by welding. The adjacent endof the tubular body I45, is likewise shouldered, and has rigidly seated thereon, as by welding, a downwardly depending operating arm I53. Thus it will be seen that a tendency to rotate the arms I52 and I53 in opposite directions will result in twisting and building up of torque in the rod I50. By virtue of this construction, the arm I53, in effect is rigidly attached to the right hand end of the torsion rod I50, and the arm I52, is in effect, connected to the left hand end of the torsion rod. In the assembly of the parts, the two arms, I52 and I53, are initially disposed at an angle to each other, and are thenmoved relatively to each other until they assume a position substantially as, seen in Fig. 8 of 'the drawings, in which condition the rod I50, has been twisted as seen in Fig. 6, so as to preload the torsion rod. The torsion rod in preloaded condition is maintained in such condition by the provision of a stop pin I55, on the arm I53, adapted to be engaged by an abutment shoulder I52, of the arm I52, to preclude rotation of said arm I52, in a clockwise direction with respect to the arm I53, as seen in Fig. 8 of the drawings. The lower end of the operating arm I53, is provided with a stud I56, carrying a roller I51, disposed in a position to be engaged by a main operating cam I59 adapted to be power driven by the motor, as will hereinafter appear. Thus, it will be apparent that with the torsion rod I50, in preloaded condition, and due to the abutment shoulder I52, of the arm I52, engaging the stop pin I55, the entire assembly attached to the rock shaft I23, in effect is adapted under certain conditions to move substantially as a single unit in the process of moving the shoe I6, toward and away from the roll I2. In the position of the parts seen in Fig. '1 of the drawings, the power driven cam I59, is disposed in relation to the roller I51, corresponding to a position at which the shoe I6, is caused to assume a position out of engagement with the roll, as seen in dotted lines in Fig. 28. To insure that the shoe moves to such position when the cam assumes the position seen in Fig. '1. we provide a coil spring I60, surrounding the tubular body I45, and having one end surrounding the rear edge of the arm I53, and the opposite end of the spring being anchored in a depending flange I of a re-enforcing channel I0 secured to the under side of the top of the sheet metal housing of the main supporting housing I0.

Shoe operating mechanism and interlocking control with roll driving mechanism The shoe operating cam I59, is fixedly secured on a power driven shaft I62, associated with driving mechanism mounted within a cast housing I63, which mechanism in turn is operably connected with and driven by the rear end extension of the shaft'of the motor 30. Said mechanism includes a main driven shaft I65, disposed in substantially axial alignment with the rear extension 30, of the motorshaft, and the said ends of said shafts are slotted as indicated at I65, and 30 respectively, to provide anchorage for the opposite ends of a coil spring I68, which constitutes a flexible coupling for transmitting power from the motor 30. to the driving mechanism within the housing I63. The use of a coil spring as a coupling has two main advantages, in that it permits accommodation to slight misalignment of the shafts being coupled, and further, in that it permits the motor to gradually assume the full load. The drive connections from the rearward end of the motor are, as will hereinafter appear, utilized to supply power for moving the shoe I6. Because the shoe is imparted oscillating motion by the cam I59, it will be apparent that when the high point D, or peak of the cam is in engagement with the roller I51, the maximum load is then being imposed upon the motor 30. In order to utilize a motor of minimum size and power requirements, we employ a fly wheel I10, on the rear-extension 30 of the motor shaft. Said wheel tends to cause the armature of the motor to continuously rotate. so that as the cam I59 is rotating in process of moving the shoe into engagement with the roll, the fly wheel effect will provide the additional force necessary, when using'a small size motor to cause the peak or high point of the cam to cam against roller I51, to cause the shoe to exert pressure against the roll. In this connection, it will also be noted that the contour of the cam I59, is such that the cam surface, with respect to the axis of the shaft I62, increases gradually, a comparatively small amount, throughout a range of approximately 180 degrees, so that the load imposed upon the motor in the movement of the shoe is gradual, and permits utilizing a motor of relatively small power size.

The cast housing I63, which contains the drive mechanism for operating the shoe, includes the rock shaft bearing I4 I, as an integral part thereof, and the housing proper is rigidly secured in position within the main housing I0, to a depending-plate I1I, by means of screws I12. The upper end of the plate I1I, has the rock shaft bearing I40, formed as an integral part thereof. as seen in Fig. l of the drawings.

The housing I63, is composed of two main cast members, I15 and I16, adapted to be connected together by machine screws I11. The driven shaft I65, of the driving mechanism is in U10 form of a headed element, and includes a portion of reduced diameter as indicated at I as clearly seen in Fig. 23, journaled in a bearing I18, press-fitted into a boss formed on the housing part I16, with the head or enlarged portion of said driven shaft disposed in abutting relation to the end of the bearing I18, and is urged in such direction, when driven by the coupler spring I68. The inner end of the reduced portion of the shaft I65 is formed as a pinion I19, which meshes with a gear I80. The gear, I80, is pressfitted on a hub member I8I, mounted on a horizontally extending shaft I62, supported at one end in a boss I15, and press-fitted at itsopposite end in a boss I16, of the respective housing members I15 and I16. The-outer end of the hub I8 I, is provided with an annular groove I8I into which.

projects a retainer plate I84, secured inposition by a screw I85. To assist in maintaining the plate I84, in proper position, said plate is formed with a projection I84, adapted to seat in a recess I86, formed in the housing member I16, as clearly seen in Fig. 24 of the drawings. Thus, the hub,

together with its gear I80, is confined against axial movement on the shaft I82. The opposite end of the hub I8I, 'is reduced in diameter and snugly telescoped into the adjacent. end of a clutch member I88, slidably mounted on the shaft I82. The inner end of the clutch member is to the gear I93, is a pinion I95, which in turn is operated by movement to the right, as viewed in Fig. 20, it shifts the trip finger 200, to the position seen in Fig. 25.of the drawings, and at which position the finger is moved out of the path of engagement with respect to the cam fingers 202, of the cam disc, and said disc is permitted to move axially on shaft I62, to the position seen meshes with a gear I96, which is rigidly secured on the cam shaft I62.

The shaft I62, is journaled in a bearing I16, of the housing member I16. Supported on the inner end of the cam shaft, as clearly seen in Fig. 22 of the drawings, is a control disc 200, which serves, as will hereinafter be described, to control the extent of intermittent rotation of the cam I59, which in turn controls movement of the shoe toward and away from the roll. The disc 200, is press-fitted on,and rigidly connected to a hub I, which in turn is splined on the extreme end of the shaft I62, so as to permit a limited amountof axial movement of the disc with said hub 20I, on said shaft I62. The disc is formed with a pair of cam fingers 202, of generally arcuate formation, as seen in Fig. 25 of the drawings, and spaced apart with respect to each other, an amount corresponding to the spacing of the high and low points on the contour ofthe cam I59. The cam fingers 202, are adapted to be engaged alternately by a spring trip finger 204,. secured in keyed'relation to the in Fig. 24 of the drawings, under influence of the coil spring 2I0, and simultaneously'therewith, the clutch member I88, is shifted into driving engagement with the clutch plate I9i. The instant that the force is removed from the rod 201, the trip finger 204, and its supporting plate "208, immediately return to the position seen in Fig. 20 of the drawings, under influence of the compression spring 2I2,. with the outer end of the trip finger disposed in position'to engag one of the cam fingers 202, causing the adjacent cam finger, during the rotation of the cam disc 200, to ride camwise upon the outer end ofthe trip finger, and thereby move the cam disc'axially outward, as clearly seen in Fig. 22 of the drawings.

shaft I62, and the shoe operating cam I59, which control the movement of the shoe I6.

It is to be understood that cam fingers 202, to .the cam I59, are such that each time that the rod 201, is operated to move end of a rock shaft 206, journaled in the housing member I16, as seen in Fig. 24 of the drawings. The opposite end of the shaft 205, projects exteriorly of the housing member I16, and has connected thereto, an arm 206, the outer end of which is connected by a rod 201, to a part of the interlocking control mechanism to be presently described. Mounted in supporting relation to the spring trip finger 204, is a plate 208, likewise ,keyed to the shaft 205. Normally the operating shoulder 204*, of the trip finger is disposed in spaced-apart relation to a slight rise or hump portion 208 of the plate 208, as seen in Fig. 19

of the drawings. 7

The marginal edge of the cam disc 200, extends into an annular groove I88, formed in the outer end of the clutch member I88, beyond the pinion I89. The cam disc, and through its connection, the clutch member I88, are urged to the position seen in Fig. 24 of the drawings by means of a coil spring 2I0, surrounding the hub 20I, of the cam disc, and re-acting at one end against the inner end face of a recess or well I15 in the housing member I15, and its opposite end seatthe trip finger 204, out of engagement with one of the cam fingers 202, the driving mechanism is set into operation for rotating the shaft I 62, and the cam I59, a portion of a revolution, which corresponds to the movement from, whatfor convenience may be designated as, a low position E of the cam I59, to the nigh position, indicated at D" of said cam I59 and vice'versa. In other words, it may be stated simply that when the trip finger 204, is disengaged, the'cam I59, moves from the position seen in Fig. 7 of the 'cular contour, provided with ing on a collar 2| I, disposed against the adjacent I face of the cam disc 200. Thus, the coil spring 2I0, in addition to exerting an axial pressureagainst the cam disc, also tends to'urge the clutch member I88, and its pinion I89, into driving relation' with the clutch plate I9I.

The trip finger 204, is normally disposed inthe position seen in Fig. 20 of the drawings, by means of a torsion spring 2I2, seated in a well H5, in the housing member I15, with one end of said spring anchored to said housing member, and the other end engaging the plate member 208,

as clearly seen in Fig. 24.'f'Said spring serves drawings to the position seen in Fig. 8 of the drawings, and the next time that the trip finger 204 is disengaged, the cam I59, is moved from the position seen in Fig. 8 of the drawings to the position seen in Fig. 7 of the drawings. As above stated, the position of the cam in Fig. 7 of the drawings corresponds to a condition wherein the shoe isba cked away or out of engagement with the roll I2, while Fig. 8 of the drawings represents a condition of the parts with the shoe disposed in ment with the roll.

Rigidly mounted on the outer end of the cam shaft-I62, is a timing disc 2I 5, of'genera1ly cira single relatively. deep marginal notch 2I6, which is disposed in close proximity to axial alignment with the low point E* of cam I59. Cooperating. with the timing disc 2I5, is an interlocking'control lever 2I8,-pivotal1y mounted on a stud. 2I9, carried by a bracket 220, fixedly secured to the adjacent Incident to such movement of the cam' disc, the clutch member I88, .is simultaneously disengaged from the clutch plate I9I, thereby the location of the cooperativ pressure engageend wall of the housing member I16, byfmeans' of screws 22I. The control lever has one end positioned immediately below and in contact with the periphery of the timing disc 2E5, and is provided with a notch N8 .to one side of which is formed an angular ,detent 222, adapted in to return the trip member and'plate to the position seen in Fig. 20, after having been moved to the position seen in Fig. 25 of the drawings, by operation of the rod 201.

It will now be apparent that when the rod 201,

certain angular positions of adjustmentof the member 2I 8 to register with and seat in the notch 2I 6, of the timing disc, as seen in Fig. 15 of the drawings. ber 2I8, is preferably formed 'of spring metal,

and is normallydisposed as seen in Fig. 13 of The interlocking lever memin and follow thecontour the drawings, exerting a slight upward pressure on the periphery of the timing disc 215. The opposite edge of the member 218, adjacent detent 222, is formed with an upstanding stop lug 225, adapted, when the member 218 is in the position as seen in Fig. 10 of the drawings, to engage the adjacent face of the timing disc 215, to limit the angular or pivotal movement of the interlocking lever member 218, in counterclockwise direction, as viewed in Figs. 10, ll, 12, and 13 of the drawings. A supporting lever 230, is pivotallymounted on the stud 219, and has its outer end connected to a control rod 231, the opposite end of which rod is connected to the depending member 108,.associated with the knee operating control member H2, as seen in Fig. 16 of the drawings. The rearward portion of themember 210, is provided with a depending lug 218 which is connected by a coil spring 233, to an upstanding lug 230 of the supporting plate 230, tending to maintain the control lever 218, and the supporting plate 230, in approximately straight line relation to each other, such as seen in Fig. 11 of the drawings.

The purpose in making control lever 218, of spring metal, is to insure against possible breakage, which might occur if the lever were rigid, and the cam 159 and timing disc 215, rotate when the detent 222, of said lever 218, is in registration with the notch 218, of said timing disc.

Mounted beneath the supporting plate 230, is a trip member 235, also connected to the operating rod 231, at one end, the opposite end being provided with an upstanding stud 233, on which is mounted a roller 231, adapted to be disposed of a cam slot indicated' at 238, formed in the supporting plate 220, as seen in Figs.1l and 13 of the drawings.

The opposite end of the stud is provided with anenlarged washer 240, overlapping the cam slot and engaging the upper surface of the plate 220, to support the roller in proper relation in the cam slot 238, as well as supporting said end of the trip member 235. The trip member 235, is provided with a depending lug 235*, to which is anchored one end of a coil spring 242, the opposite end of which sprin is anchored to a depending lug 230, of the supporting plate 230. Thisspring connection serves to maintain the roller 231 in yielding engagement with the cam surface of the slot 238, and causes the roller to follow the contour of such surface during the movement of the trip member 235, as may be seen in Figs. 10, 11, 12, and 13 of the drawings.

Also mounted on lever 245, which includes a leg portion 245*, slidably mounted on the rod 201, and normally disposed in abutting relation to a nut 201 on the outer end of said rod. Said trip member also includes an upstanding lug v245 projecting through an aperture 220 in the supporting plate 220, and adapted to abut against aned'ge of the opening as seen in for limiting the position of the trip lever 245, in'one direction of movement. The trip lever also includes an arm 245, provided with a depending lug 245 adapted in the position seen in Fig. 11 to engage the depending lug 235, of the member 235.

The control lever 218, supporting lever 230, and the trip lever 245, are held in assembled relation, against the bracket 220,'on the pivot pin 219, by a coil spring 219 The spring surrounds a' sleeve 219, on the pin, and abuts at the pivot pin 219, is a trip' Fig. 10 of the drawings,-

- against the roll.

one end against the underside of the control lever 218, and at the other end against a washer 219, abutting the end of the sleeve, and the parts are held in such assembled relation by a spring clip 219 as seen in Figs. 14 and 16 of the drawings.

As above described, when the rod 201, is pulled, for example, from the position seen in Fig. 10 of the drawings, to the position seen in Fig. 12 of the drawings, the trip finger 204, is disengaged, and the motor power is then coupled with the clutch 188, for driving the cam shaft 162, and the cam 159, as above described, and which, as clearly above stated, completes a partial revolution each time the trip finger 204, is disengaged. The design of the parts is such, that during two successive actions of the trip finger. the cam 159, completes a single revolution.

Operation The interlocking control mechanism between the drives for the roll and the shoe respectively, assumes several different positions of adjustment during the cycle of operation of the machine. When the knee control member 112, is in the dotted line position indicated at A, the drive mechanisms for both the roll and shoe are in inoperative position, and at which position the shoe is either in pressure engagement with the roll, or is disposed out of engagement with the roll. If we assume that the shoe is away from the roll, and the knee control lever 1 12, is moved from the position indicated at A" to the position indicated at B in Fig. l, the interlocking control mechanism first assumes the position as seen in Fig. 12 of the drawings, and finally assumes the position seen inFig. 13 of the drawings. When pressure on the knee control 112, is then relieved so as to permit said member 1 12 to assume again the position A, the interlocking control mechanism acquires a position as seen in Fig. 11 of the drawings, during which movement, the rod 201 is operated to disengage trip finger204, and partial rotation of cam 159, is effected for moving the shoe If pressure is additionally released on the knee control 112, so as to permit it to assume the full line position indicated at C in Fig. 1 of the drawings, the interlocking control mechanism then acquires the position seen in Fig. I

10 of the drawings, during which movement the shoe is in engagement with the roll, and movementv is transmitted to the members 108 and 106, which effects engagement of the clutch 51 of the roll driving mechanism for causing the roll to rota e.

It is to be understood that when, however, the knee control lever is held at the position indicated at A, the roll is stationary, and the shoe is in pressure engagement therewith, so as t perform a pressing operation on articles being worked upon, whereas, when the control member 1 12 is permitted-to move to the position seen in full lines at C," the articles being worked upon are caused to be ironed, with the roll rotating against the face of the shoe, and the latter in pressure engagement with the roll.

Now, when the knee lever 112, is again moved to, the position indicated at A," the interlocking control mechanism during this interim assumes a position as seen in Fig. 11 of the drawings, and during the movement from position.C to A," the clutch for driving the roll 12, is again disengaged, and theroll arrested, and when the control- 

